EP3149353B1 - Frein à disque, étrier de frein et jeu de plaquettes de frein pour un frein à disque - Google Patents

Frein à disque, étrier de frein et jeu de plaquettes de frein pour un frein à disque Download PDF

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Publication number
EP3149353B1
EP3149353B1 EP15723529.2A EP15723529A EP3149353B1 EP 3149353 B1 EP3149353 B1 EP 3149353B1 EP 15723529 A EP15723529 A EP 15723529A EP 3149353 B1 EP3149353 B1 EP 3149353B1
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EP
European Patent Office
Prior art keywords
brake
contact surface
pair
disc
brake pad
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP15723529.2A
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German (de)
English (en)
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EP3149353B2 (fr
EP3149353A1 (fr
Inventor
Tobias Fischl
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Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
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Knorr Bremse Systeme fuer Nutzfahrzeuge GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F16D55/2265—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes the axial movement being guided by one or more pins engaging bores in the brake support or the brake housing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/005—Components of axially engaging brakes not otherwise provided for
    • F16D65/0068—Brake calipers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
    • F16D65/567—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc brake
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
    • F16D65/567—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc brake
    • F16D65/568—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc brake for synchronous adjustment of actuators arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0016—Brake calipers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/22—Mechanical mechanisms converting rotation to linear movement or vice versa acting transversely to the axis of rotation
    • F16D2125/26—Cranks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/22—Mechanical mechanisms converting rotation to linear movement or vice versa acting transversely to the axis of rotation
    • F16D2125/28—Cams; Levers with cams
    • F16D2125/32—Cams; Levers with cams acting on one cam follower

Definitions

  • the invention relates to a disc brake according to the preamble of claim 1.
  • the invention also relates to a caliper and a brake pad set.
  • a disc brake In the typical design of a disc brake, this consists of a caliper together with internal mechanics, usually two brake pads and the brake disc.
  • the internal mechanics are transmitted via a power source, e.g. via a pneumatically actuated cylinder, introduced forces, reinforced by an eccentric mechanism and as clamping force via threaded pipes, which also threaded bush, threaded spindles, pressure stamp oa. be called, transferred with pressure pieces on brake pads and brake disc, which is compensated through the threaded tubes wear of brake disc and brake pads.
  • a distance between the brake pads and the brake disc is called a clearance. Deceleration is largely determined by the coefficient of friction between the brake disc and brake pad. Since the pads are structurally designed as wearing parts and the coefficients of friction are dependent on the strength, they are generally softer than the brake disc, i. the pads learn about their service life, a change in the lining thickness, they wear out. As a result of this pad wear and additional disc wear this clearance is larger. From this covering strength change, there is the necessity that a wear adjustment compensates for the change and thus sets a constant clearance.
  • the application forces act on both brake pads on the brake disc, which undergoes a delay of the rotational movement in dependence on the amount of the application force.
  • the brake lining which lies on the application side of the brake disc, is called zuspann nurse brake pad.
  • the other brake pad is located on the other side of the brake disc and is in contact with a saddle back of the caliper.
  • the application-side lining is moved in the direction of the brake disk. Once this is in contact with the brake disc, the caliper is moved by the resulting counterforce with the back-side brake pad in the direction of the brake disc. If now the back-side brake pad also touches the brake disc, a braking effect is generated.
  • the back-side brake pad rests against the seat back of the caliper on a flat-milled surface.
  • This surface has approximately the shape of the back-side brake pad.
  • the application side brake pad is e.g. pressed to the brake disc via two threaded tube units. In this case, it is considered disadvantageous that in this case an uneven wear of the brake pads may occur
  • a disc brake according to the preamble of claim 1 starts, for example DE-B-10 2006 034 766 out.
  • the object of the present invention is therefore to provide an improved disc brake.
  • Another object is to provide an improved caliper.
  • Yet another object is to provide an improved brake pad set.
  • a disc brake according to the invention preferably pneumatically operated, is apparent from claim 1.
  • the projection corresponds with the one contact surface of the at least one pair of contact surfaces and the recess with the other contact surface of the at least one pair of contact surfaces with each other and act in the installed state positively together.
  • the projection is received in the recess, whereby the back-side brake pad is advantageously hindered from unscrewing from the brake caliper.
  • the projection with the one contact surface of the at least one pair of contact surfaces and the recess with the other contact surface of the at least one pair of contact surfaces may have a circular cross-section.
  • the recess is easy to produce, e.g. by drilling and / or turning out.
  • the projection with one contact surface of the at least one pair of contact surfaces and the recess with the other contact surface of the at least one pair of contact surfaces may have an oval or polygonal cross section. This results in the advantage that a likelihood of confusion is reduced by this unique assignment.
  • the projection is integrally formed with the one contact surface of the at least one pair of contact surfaces on the saddle back of the caliper, and the recess is formed with the other contact surface of the at least one pair of contact surfaces in the brake pad carrier of the back side brake pad.
  • the production cost of the projections on saddle back eg by milling, compared to a conventional, milled plan contact surface is not expensive.
  • the projection with the one contact surface of the at least one pair of contact surfaces projects from the saddle back of the caliper from a machined free surface in the direction of the brake disk. The manufactured open space allows weight savings.
  • the disc brake further comprises a brake application device, preferably with a brake rotary lever, and at least one threaded tube unit with at least one threaded tube with a central axis.
  • the projection having one abutment surface of the at least one pair of abutment surfaces and the recess with the other abutment surface of the at least one pair of abutment surfaces are mutually coaxial with their centerlines and coaxial with the central axis of the at least one threaded tube assembly.
  • the disc brake further comprises an application device, preferably with a brake rotary lever, and at least two threaded tube units each having at least one threaded tube, each having a central axis.
  • a first projection having one abutment surface of the at least one pair of abutment surfaces and a first recess having the other abutment surface of the at least one pair of abutment surfaces are mutually coaxial with their centerlines and coaxial with the central axis of the one of the at least two threaded tube assemblies, and a second protrusion with the other bearing surface of the at least one pair of abutment surfaces and a second recess with the other abutment surface of the at least one pair of abutment surfaces are arranged mutually coaxial with their center lines and coaxial with the central axis of the other of the at least two threaded tube units.
  • the two individual abutment surfaces are arranged in the same central axes as those of the threaded tube units on the application side. This results in the advantage of a reduction of lever arms in the saddle back with respect to tension struts of the caliper. Unequal wear of the brake pads is advantageously significantly reduced.
  • the disc brake has an adjusting device, which is inserted into a threaded tube on. This makes a compact design possible.
  • An inventive caliper of the disc brake described above has a saddle back with a transverse portion extending parallel to the brake disc and perpendicular to the brake disc axis, wherein the transverse portion on the side facing the brake disc, a ganabitesschi with at least one projection with the one Contact surface of the at least one pair of contact surfaces.
  • An inventive brake lining set for the disc brake described above has at least one application-side brake pad and at least one back-side brake pad, wherein the back-side brake pad at least one recess for receiving a corresponding projection with the at least one recess.
  • the brake pad set further includes a pad retaining bracket, wherein the at least one application-side brake pad and the at least one back-side brake pad are each provided with a pad retaining spring.
  • Fig. 1 shows a schematic partial sectional view of a conventional disc brake 1 in a plan view.
  • Fig. 1a is a plan view of the conventional disc brake 1 is shown.
  • Fig. 2 shows a schematic partial sectional view of a conventional caliper 8 of the conventional disc brake 1 after Fig. 2 , in which Fig. 3 a schematic perspective view of a conventional back-side pad 50 of a conventional brake pad set of the conventional disc brake 1 after Fig. 2 represents.
  • the disk brake 1 has a brake disk 2 with a brake disk axis 3.
  • a zuspannseite Z of the brake disc 2 is a zuspannduser brake pad 40, which comprises a brake pad carrier 4 and a friction lining 5 mounted thereon.
  • Another, back-side brake pad 50 is disposed on a rear side R of the brake disc 2.
  • the back-side brake pad 50 also includes a brake pad carrier 6 and a friction lining 7 mounted thereon. These two brake pads 40 and 50 form a brake pad set.
  • the brake disk 2 is overlapped by a, designed here as floating caliper, brake caliper 8.
  • the brake caliper 8 comprises an application section 9, a saddle back 10 and two tension struts 11, 12.
  • the application section 9 is located on the application side Z and receives an application mechanism of the disc brake 1. The application mechanism will be explained below.
  • the saddle back 10 is arranged on the back R side.
  • the tension struts 11 and 12 are arranged above the brake disk 2 and extend parallel to one another and to the brake disk axis 3.
  • the application portion 9 and the seat back 10 are fixedly connected to one another by the tension struts 11, 12 and connected thereto, e.g. formed as a one-piece casting.
  • the disc brake 1 is here as a two-stamp brake with two threaded tube units 14 and 14 ', each with a threaded tube 15, 17 is formed.
  • the threaded pipes 15, 17 may also be referred to as threaded pistons, threaded spindles or pressure spindles.
  • the application-side brake pad carrier 4 is connected to the threaded tubes 15, 17 of the threaded tube units 14, 14 'each via a pressure piece 16, 18 in connection.
  • the pressure piece 16 is attached to one end of the threaded tube 15, and the pressure piece 18 is connected to one end of the threaded tube 17.
  • the back-side brake pad 50 is also called reaction-side brake pad 50 and is set with its brake pad carrier 6 on the other side of the brake disc 2, ie on the back side, in the brake caliper 8.
  • the side of the brake lining carrier 6, which is not provided with the friction lining 7, is in contact with the saddle back 10 via a transverse section 13.
  • the transverse section 13 extends parallel to the brake disk 2 and at right angles to the brake disk axis 3.
  • the transverse section 13 is provided on the side which faces the brake pad carrier 6 of the back-side brake pad 50 with an abutment section carrier 130 on which a contact surface 131 (see also FIGS Fig. 2 ) arranged with a contact surface 132 (see also Fig. 3 ) of the brake pad carrier 6 of the back-side brake pad 50 is in contact.
  • the brake pads 40 and 50 are guided in recordings, not shown, and held by a pad retaining bracket 25, not described in detail, which is in contact with a respective one on the top of each brake pad carrier 4, 6 mounted pad retaining spring 26, 27.
  • the pad retaining clip 25 is held with an application-side end in an unsigned receptacle on Zuspannabêt 9 of the caliper 8 and fastened with its other, back-side end of a pad retaining bracket 28 on saddle back 10 of the caliper 8. This is in Fig. 1a shown.
  • the threaded tubes 15, 17 each have an external thread and are each arranged rotatable in a bridge 21 in associated internal threads.
  • the bridge 21 is also referred to as traverse.
  • the bridge 21 and thus the threaded tubes 15, 17 are actuated by a clamping device, here a brake rotary lever 22 with a pivot axis perpendicular to the brake disc axis 3.
  • the brake rotary lever 22 has an unspecified lever body, which is in cooperation with the bridge 21.
  • the brake rotary lever 22 is here also in operative connection with a compressed air cylinder, not shown, wherein the compressed air cylinder is connected to a connection section 29 (FIG. Fig. 1a ) of the caliper 8 is mounted.
  • the bridge 21 is adjustable in the direction of the brake disk axis 3 by the brake rotary lever 22.
  • a movement on the brake disc 2 is referred to as Zuspannschul, and a movement in the opposite direction is called release movement.
  • a return spring 23 is received in the middle of the bridge 21 in a corresponding recess on the lining side of the bridge 21 and is supported on the brake caliper 8. By means of the return spring 23, the bridge 21 in the release movement in the in Fig. 1 and 1a shown dissolved position of the disc brake 1 back adjusted.
  • the disc brake 1 may have different power drives.
  • the brake rotary lever 22 is pneumatically actuated here, for example.
  • For construction and function of a pneumatic disc brake 1 is to the corresponding description of DE 197 29 024 C1 directed.
  • a distance between the friction linings 5, 7 and the brake disc 2 in the released position is referred to as a clearance.
  • this clearance is larger. If this is not compensated, the disc brake 1 can not reach its peak performance because an actuation stroke of the actuation mechanism, i. Here the actuation stroke or a pivot angle of the brake rotary lever 22, is no longer sufficient.
  • an adjusting device 19 is inserted coaxially with the central axis 14a.
  • the term "reenactment” is to be understood as a clearance reduction.
  • the predetermined clearance is determined by the geometry of the disc brake 1 and has a so-called constructive clearance.
  • the adjusting device 19 reduces an existing clearance, if it is too large with respect to the predetermined clearance, to the target value of the predetermined clearance.
  • a detailed description of such an adjustment device 19 can the document DE 10 2004 037 771 A1 be removed.
  • the lower threaded tube unit 14 ' is provided with a cam 20, which is arranged coaxially with the lower threaded tube unit 14', to the threaded tube 17 and the driving axle 14 'a.
  • the driver 20 is inserted here in the threaded tube 17 and is in operative connection with this.
  • the center axes 14a, 14'a and the brake disk axis 3 are arranged parallel to each other.
  • the adjusting device 19 is connected via an unspecified drive with the brake rotary lever 22 in cooperation.
  • the adjusting device 19 and the driver 20 are coupled by a synchronization unit 24 such that a rotational movement of the threaded tube 15 about its central axis 14a causes a rotational movement of the threaded tube 17 about the central axis 14'a and vice versa.
  • the synchronization unit 24 will not be explained further here. With it is a synchronous movement of the threaded tubes 15 and 17 of the threaded tube units 14 and 14 'at readjustments (and possibly reset operations, depending on the nature of the adjusting device 19, which can also be designed to increase a clearance) and settings during maintenance, e.g. Brake lining change, (manual drive, for example via an operating end of the driver 20 and / or a drive section of the adjusting device 19 guaranteed.
  • the required application force is generated via the eccentric to the threaded tube units 14, 14 'mounted brake rotary lever 22 and transmitted to the bridge 21.
  • the so applied to the bridge 21 application force is then through the two threaded tube units 14, 14 ', the threaded tubes 15, 17 with the pressure pads 16, 18 on the brake pad carrier 4 of the application side brake pad 40 and the caliper 8 also on the brake pad carrier 6 of the back Brake pads 50 and then transferred to the brake disc 2.
  • the threaded tube units 14, 14 ' are moved in the direction of the brake disc 2.
  • the brake caliper 8 with the back-side brake pad 50 is also moved counter to the direction of the application-side brake pad 40 in the direction of the brake disk 2 due to the resulting opposing force.
  • a braking effect is generated.
  • the back-side brake pad 50 rests with its contact surface 132 against the abutment surface 131 of the abutment portion carrier 130 of the transverse section 13 of the saddle back 10 of the caliper 8.
  • the back-side brake pad 50 is in Fig. 3 with view of its contact surface 132 shown.
  • the contact surface 132 is at the clearly visible here outside of the brake pad carrier 6 of the back-side brake pad 50 arranged.
  • the contact surface 131 of the saddle back 10 is machined, eg milled, manufactured.
  • This contact surface 131 is in Fig. 2 clearly visible and has approximately the shape of the brake pad carrier 6 of the back-side brake pad 50.
  • the application-side brake pad 40 is in contact with its brake pad carrier 4 with the pressure pieces 16, 18 of the threaded tube units 14, 14 'arranged at a distance from one another.
  • imagined force introduction lines run in the direction of the central axes 14a, 14'a in parallel on both sides at a distance from the brake disk axis 3.
  • a very unfavorable leverage in the application of force is generated by the full-surface support of the back-side brake pad 50 on the plant section carrier 130 of the transverse section 13 on saddle back 10 of the caliper 8.
  • a point of application 61 of the introduction of force with an arrow which is intended to indicate a counterforce 60 of the back-side brake pad 50, in Fig. 1a located.
  • the two lever arms 62, 62 'meet in the point of application 61 which lies directly in a plane perpendicular to the plane extending vertical plane of the brake disc axis 3.
  • each lever arm 62, 62 ' is each connected to a likewise dash-double dotted line, each one symbolized by the tension struts 11, 12 tensile force direction 63, 63'.
  • the length of each lever arm 62, 62 ' corresponds approximately to half the length of the transverse section 13 of the saddle back 10th
  • Fig. 4 is a schematic partial sectional view of an embodiment of a brake caliper 8 according to the invention a disc brake 1 according to the invention shown.
  • Fig. 5 shows a schematic perspective view of the embodiment of the caliper 8 according to the invention Fig. 4
  • Fig. 6 is a schematic perspective view of a brake pad 50 'according to the invention shown.
  • Fig. 7 a schematic plan view of an embodiment of a disc brake 1 according to the invention with the brake caliper 8 according to the invention Fig. 5 and with a brake pad set according to the invention with the brake pads 40 and 50 '.
  • the projections 30, 32 each have a contact surface 31, 33 on their end faces facing the brake disk 2. These two contact surfaces 31, 33 lie together in one plane.
  • the projections 30, 32 circular cylindrical dome and the contact surfaces 31, 33 are formed as circular surfaces.
  • the projections 30, 32 are arranged to the brake disc axis 3 on both sides with the same distance.
  • the center lines of the circular abutment surfaces 31, 33 are each coaxial with the center axes 14a, 14'a of the threaded tube units 14, 14 'of the application side. This is in Fig. 7 clearly visible.
  • the center line of the threaded tube unit 14 is the central axis 14a and extends both as a center line through the pressure piece 16 of the application-side brake pad 40 and as a center line through the center of the circular contact surface 31 of the projection 30 of the saddle back 10.
  • Fig. 6 shows the associated back-side brake pad 50 'with the brake pad carrier 6' and the friction lining 7.
  • the outer back side of the brake pad carrier 6 ' has an open surface 39, but in contrast to the usual brake pad after Fig. 3 no contact surface for the saddle back 10 of the caliper 8 forms.
  • this free surface 39 are in this example circular cylindrical recesses 35, 37, each with a circular contact surface 36, 38, each forming a bottom surface of such a recess 35, 37, formed.
  • the circular cylindrical recesses 35, 37 correspond with the circular cylindrical projections 30, 32 of the saddle back 10 after Fig. 4 and 5 ,
  • the free surfaces 34, 39 also allow a weight reduction of the caliper 8 as well as the entire disc brake. 1
  • the back-side brake pad 50 ' has the pad retaining spring 27 on the upper side of the brake pad carrier 6'.
  • the friction lining 7 is applied to the side of the brake pad carrier 6 ', which is opposite to the outer back side with the recesses 35, 37 of the brake pad carrier 6'.
  • the free surface 34 of the contact section support 130 of the saddle back 10 is milled flat, wherein the cost of machining to the usual plant section support 130 of the conventional saddle back 10 after Fig. 2 remains unchanged.
  • the contact pressure of the back-side brake pad 50 'and the application-side brake pad 40 is adjusted because the imaginary force introduction lines at the rear-side brake pad 50 with the center lines 14a, 14'a and thus aligned with the imaginary force introduction lines of the threaded tube units 14, 14 'at the application-side brake pad 40 and match.
  • An inventive brake pad set of the disc brake 1 according to the invention Fig. 7 comprises the application-side brake pad 40 and the back-side brake pad 50 ', which has the brake pad carrier 6' with the recesses 35, 37 for the projections 30, 32 of the saddle back 10.
  • the brake pads 40, 50 ' can be installed without any kind of confusion. This is ensured by the fact that the outer diameter of the pressure pieces 16, 18 are greater than the outer diameter of the recesses 35, 37.
  • the shape of the projections 30, 32 and recesses 35, 37 instead of a circular cross-section transverse to the center line have an oval or / and angular cross-section.
  • the cross sections of all protrusions 30, 32 and recesses 35, 37 may be possible for these cross sections of all protrusions 30, 32 and recesses 35, 37 to have the same or different shape, e.g. the cross sections of the projection 30 and recess 37 are circular and of projection 32 and recess 35 oval.
  • the brake pad carrier 4 of the application-side brake pad 40 is provided with recesses for the pressure pieces 16, 18.
  • the can Plungers 16, 18 and the projections 30, 32 have different diameters and / or shapes for unmistakable installation of the brake pads 40, 50 '.
  • the projections 30, 32 and the associated recesses 35, 37 may also be arranged in the opposite way, i. the projections 30, 32 are arranged on the brake pad carrier 6 ', whereas the recesses 35, 37 are formed in the seat back 10 of the caliper 8. It is also a combination of a projection 30 and a recess 37 on the brake pad carrier 6 'conceivable, wherein the associated combination of projection 31 and recess 35 is arranged on the saddle back 10.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Claims (11)

  1. Frein (1) à disque, de préférence à actionnement à l'air comprimé, notamment pour un véhicule automobile, comportant un disque (2) de frein ayant un axe (3) de disque de frein, un étrier (8) de frein, notamment un étrier coulissant, ayant une partie (9) de serrage et un dos (10) d'étrier, qui sont reliés par des tirants (11, 12), comportant, en outre, un système de serrage, ayant de préférence un levier (22) tournant de frein et au moins une unité (14, 14') à tube fileté, ayant au moins un tube (15, 16) fileté à axe (14a, 14'a) médian, au moins deux garnitures (40, 50, 50') de frein, ayant chacune un porte-garniture (4, 6, 6') de frein, dans lequel, parmi les garnitures (40, 50, 50') de frein, une garniture (40) de frein du côté du serrage est associée à la partie (9) de serrage et une garniture (50, 50') de frein du côté du dos est associée au dos (10) de l'étrier, dans lequel le porte-garniture (6, 6') de frein de la garniture (50, 50') de frein du côté du dos et le dos (10) de l'étrier (8) de frein sont en contact, par au moins une paire de surfaces (31, 33 ; 36, 38 ; 131, 132) de contact, l'une des surfaces (31, 33) de contact de la au moins une paire de surfaces (31, 33 ; 36, 38) de contact étant une surface frontale d'une saillie (30, 32) et en ce que l'autre surface (36, 38) de contact de la au moins une paire de surfaces (31, 33 ; 36, 38) de contact est une surface de fond d'un évidement (35, 37),
    caractérisé en ce que
    la saillie (30, 32), ayant la une surface (31, 33) de contact de la au moins une paire de surfaces (31, 33 ; 36, 38) de contact, et l'évidement (35, 37), ayant l'autre surface (36, 38) de contact de la au moins une paire de surfaces (31, 33 ; 36, 38) de contact, sont disposés entre eux coaxialement à leurs lignes médianes et coaxialement à l'axe (14a, 14'a) médian de la au moins une unité (14, 14') de tube fileté et en ce que
    la saillie (30, 32), ayant la une surface (31, 33) de contact de la au moins une paire de surfaces (31, 33 ; 36, 38) de contact, dépasse d'une surface (34) libre du dos (10) de l'étrier, la surface (34) libre ne formant pas de surface de contact pour la garniture (50') de frein du côté du dos.
  2. Frein à disque suivant la revendication 1, caractérisé en ce que la saillie (30, 32), ayant la une surface (31, 33) de contact de la au moins une paire de surfaces (31, 33 ; 36, 38) de contact et l'évidement (35, 37), ayant l'autre surface (36, 38) de contact de la au moins une paire de surfaces (31, 33 ; 36, 38) de contact, se correspondent entre eux et coopèrent à complémentarité de forme entre eux à l'état monté.
  3. Frein à disque suivant la revendication 1 ou 2, caractérisé en ce que la saillie (30, 32), ayant la une surface (31, 33) de contact de la au moins une paire de surfaces (31, 33 ; 36, 38) de contact, et l'évidement (35, 37), ayant l'autre surface (36, 38) de contact de la au moins une paire de surfaces (31, 33 ; 36, 38) de contact, ont une section transversale circulaire.
  4. Frein à disque suivant l'une des revendications 1 ou 2, caractérisé en ce que la saillie (30, 32), ayant la une surface (31, 33) de contact de la au moins une paire de surfaces (31, 33 ; 36, 38) de contact, et l'évidement (35, 37), ayant l'autre surface (36, 38) de contact de la au moins une paire de surfaces (31, 33 ; 36, 38) de contact, ont une section transversale ovale ou polygonale.
  5. Frein à disque suivant l'une de revendications précédente, caractérisé en ce que la saillie (30, 32), ayant la une surface (31, 33) de contact de la au moins une paire de surfaces (31, 33 ; 36, 38) de contact, vient de matière avec le dos (10) de l'étrier (8) de frein et en ce que l'évidement (35, 37), ayant l'autre surface (36, 38) de contact de la au moins une paire de surfaces (31, 33 ; 36, 38) de contact, est formé dans le porte-garniture (6') de frein de la garniture (50') de frein du côté du dos.
  6. Frein à disque suivant la revendication 5, caractérisé en ce que la saillie (30, 32), ayant la une surface (31, 33) de contact de la au moins une paire de surfaces (31, 33 ; 36, 38) de contact, dépasse, en direction du disque (2) de frein, d'une surface (34) libre usinée sur le dos (10) de l'étrier de frein.
  7. Frein à disque suivant l'une des revendications 1 à 6, comportant, en outre, un dispositif de serrage, ayant, de préférence, un levier (22) tournant de frein, et au moins deux unités (14, 14') de tube fileté, ayant chacune au moins un tube (15, 16) fileté, ayant, respectivement, un axe (14a, 14'a) médian, caractérisé en ce qu'une première saillie (30), ayant la une surface (31) de contact de la au moins une paire de surface (31 ; 38) de contact, et un premier évidement (37), ayant l'autre surface (38) de contact de la au moins une paire de surfaces (31 ; 38) de contact, sont disposés entre eux coaxialement à leurs axes médians et coaxialement à l'axe (14a) médian de l'une des au moins deux unités (14, 14') de tube fileté et en ce qu'une deuxième saillie (32), ayant l'autre surface (33) de contact de la au moins une paire de surfaces (33 ; 36) de contact, et un deuxième évidement (35), ayant l'autre surface (36) de contact de la au moins une paire de surfaces (33 ; 36) de contact, sont disposés entre eux coaxialement à leurs axes médians et coaxialement à l'axe (14'a) médian de l'autre des au moins deux unités (14, 14') de tube fileté.
  8. Frein à disque suivant l'une des revendications précédentes, comportant, en outre, un dispositif (19) de rattrapage, qui est inséré dans un tube (15, 17) fileté.
  9. Etrier (8) de frein d'un frein (1) à disque suivant l'une des revendications précédentes, caractérisé en ce que le dos (10) de l'étrier (8) de frein a une section (13) transversale, qui s'étend parallèlement au disque (2) de frein et perpendiculairement à l'axe (3) du disque de frein, la section (13) transversale ayant, du côté tourné vers le disque (2) de frein, un support (130) de partie de contact, ayant au moins une saillie (30, 32), ayant la première surface (31, 33) de contact de la au moins une paire de surfaces (31, 33 ; 36, 38) de contact.
  10. Jeu de garniture de frein d'un frein (1) à disque suivant l'une des revendications 1 à 8, comportant au moins une garniture (40) de frein du côté du serrage et au moins une garniture (50') de frein du côté du dos, la garniture (50') de frein du côté du dos ayant au moins un évidement (35, 37) de réception d'une saillie (30, 31) correspondant au au moins un évidement (35, 37).
  11. Jeu de garniture de frein suivant la revendication 10, caractérisé en ce que le jeu de garniture de frein comprend, en outre, un pontet (25) de maintien de garniture, dans lequel la au moins une garniture (40) de frein du côté du serrage et la au moins une garniture (50') de frein du côté du dos sont pourvues chacune d'un ressort (26, 27) de maintien de garniture.
EP15723529.2A 2014-05-26 2015-05-20 Frein à disque, étrier de frein et jeu de plaquettes de frein pour un frein à disque Active EP3149353B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014107401.7A DE102014107401A1 (de) 2014-05-26 2014-05-26 Scheibenbremse, Bremssattel und Bremsbelagsatz für eine Scheibenbremse
PCT/EP2015/061189 WO2015181033A1 (fr) 2014-05-26 2015-05-20 Frein à disque, étrier de frein et jeu de plaquettes de frein pour un frein à disque

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EP3149353A1 EP3149353A1 (fr) 2017-04-05
EP3149353B1 true EP3149353B1 (fr) 2019-07-10
EP3149353B2 EP3149353B2 (fr) 2023-03-08

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US (1) US10316916B2 (fr)
EP (1) EP3149353B2 (fr)
JP (1) JP6346310B2 (fr)
KR (1) KR20170013301A (fr)
CN (1) CN106489039B (fr)
AU (1) AU2015266171B2 (fr)
CA (1) CA2950455A1 (fr)
DE (1) DE102014107401A1 (fr)
MX (1) MX2016015422A (fr)
RU (1) RU2666984C1 (fr)
WO (1) WO2015181033A1 (fr)
ZA (1) ZA201608728B (fr)

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ZA201608728B (en) 2017-09-27
JP2017516958A (ja) 2017-06-22
US20170074338A1 (en) 2017-03-16
WO2015181033A1 (fr) 2015-12-03
RU2666984C1 (ru) 2018-09-13
EP3149353B2 (fr) 2023-03-08
KR20170013301A (ko) 2017-02-06
US10316916B2 (en) 2019-06-11
CA2950455A1 (fr) 2015-12-03
JP6346310B2 (ja) 2018-06-20
CN106489039A (zh) 2017-03-08
CN106489039B (zh) 2019-04-19
DE102014107401A1 (de) 2015-11-26
AU2015266171B2 (en) 2018-11-15
MX2016015422A (es) 2017-03-23
AU2015266171A1 (en) 2016-12-08
EP3149353A1 (fr) 2017-04-05

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